JP2012107725A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a continuously variable transmission capable of improving inconvenience on a conventional continuously variable transmission and restraining a gap of a rotary axis of a rolling member.SOLUTION: In the continuously variable transmission 1 including first and second rotation members 10, 20 which are oppositely arranged and are relatively rotatable around a common first rotation axis R1, a sun roller 30, a carrier 40, a plurality of planetary balls 50 held by the first and second rotation members 10, 20 and radially arranged, and support shafts 51 having the same second rotation axes R2 as those for the planetary balls 50 and projecting both ends from the planetary balls 50, wherein the carrier 40 guides both ends of the support shafts 51 by radial guide grooves 43 of a first disk section 41 and radial guide grooves 44 of a second disk section 42, radii of corner round sections C1, C2 of respective guide grooves 43, 44 at boundary sections among groove sidewalls 43a, 44a and ends 43c, 43d, 44c, and 44d in a radial direction are set up to be a radius or below of the support shaft 51.

Description

  The present invention includes an input-side rotating element and an output-side rotating element having a common rotating shaft, and a plurality of rolling members arranged radially with respect to the rotating shaft, and is sandwiched between the rotating elements. The present invention relates to a continuously variable transmission that continuously changes a transmission gear ratio between input and output by tilting a rolling member.

  Conventionally, this type of continuously variable transmission, that is, a shaft as a rotating shaft, a plurality of rotational elements that can rotate relative to the central axis of the shaft as a first rotating central axis, and a parallel to the first rotating central axis And a plurality of rolling members radially arranged around the first rotation center axis, the first rotation element on the input side and the output side on the output side. Each rolling member is clamped by the second rotating element, and each rolling member is disposed on the outer peripheral surface of the third rotating element, and the gear ratio is continuously changed by tilting the rolling member. A continuously variable transmission of a so-called traction planetary gear mechanism is known. This continuously variable transmission also includes a fourth rotating element that holds each rolling member via a respective rotating shaft. When the rolling member is tilted, each end of its own rotating shaft is the fourth. It is guided along the guide groove on the input side and the guide groove on the output side in the rotating element. For example, Patent Documents 1 and 2 below disclose this type of continuously variable transmission. In the continuously variable transmission of Patent Document 1, the guide groove on the input side and the guide groove on the output side provided in the cage (carrier) as the fourth rotating element are offset in the circumferential direction when viewed in the axial direction of the shaft, A parallel state between the first rotation center axis and the second rotation center axis is maintained. One of the guide grooves facing each other in the axial direction is a groove in which both ends in the radial direction are closed, and the other is a groove in which both ends in the radial direction are opened. Further, Patent Document 2 discloses a continuously variable transmission in which a long window-shaped guide hole that is elongated in the radial direction functions as a guide groove.

JP 2010-144932 A JP 2002-250421 A

  Here, the relationship between the rolling member and the carrier (fourth rotating element) will be described. In this type of continuously variable transmission, the carrier includes two disk members arranged concentrically facing each other, and a plurality of connecting shafts that connect the respective disk members, and has a bowl shape as a whole. It is formed to become. Each rolling member is radially arranged in the inner space of the carrier with the rotation axis of the carrier as the center. The rolling member is provided with a support shaft that enables rotation, and both ends of the rolling member are held by the carrier by inserting them into the guide grooves of the respective disk members. The guide grooves are formed radially on the respective disk members according to the position of the rolling member, and guide the end of the support shaft in the radial direction of the carrier when the rolling member is tilted. In the continuously variable transmission of the above-mentioned Patent Document 1, the guide grooves are offset and arranged so that the support shaft can be moved in the tilt direction along the guide grooves. A tilting operation of the second rotation center axis in a plane including the second rotation center axis is realized. However, when both ends in the radial direction of the guide groove are closed or in the case of the guide slot in Patent Document 2, when the support shaft reaches the radial end of the guide slot or guide slot. In addition, the second rotation center axis may deviate from the above plane. This is because the boundary between the side wall of the guide groove and the end in the radial direction due to manufacturing reasons in the die-cutting process and cutting process at the time of manufacture for the guide groove and the like, and for avoiding stress concentration. This is because there is a possibility that the support shaft may move along the corner radius portion if the corner radius portion is larger than the radius of the support shaft. Such a deviation of the second rotation center axis causes a rotation axis deviation of the rolling member and causes a skew. Therefore, in a continuously variable transmission, power transmission efficiency is reduced due to an unintended shift or generation of heat loss. there is a possibility.

  Therefore, an object of the present invention is to provide a continuously variable transmission that can improve the disadvantages of the conventional example and suppress the rotational axis deviation of the rolling member.

  In order to achieve the above object, the present invention provides a first and a second rotating element having a common first rotation center axis arranged opposite to each other and capable of relative rotation, and a second parallel to the first rotation center axis. A rolling member having a rotation center axis, which is arranged in a radial manner around the first rotation center axis and sandwiched between the first and second rotation elements; the first rotation element; By changing the respective contact points with the moving members and the respective contact points between the second rotating element and the rolling members by the tilting operation of the rolling members, the rotation ratio between the rotating elements can be changed. A shift control unit to be changed, each rolling member is disposed on an outer peripheral surface, and a third rotation element capable of relative rotation with respect to the first and second rotation elements on the first rotation center axis; A support shaft of the rolling member having a second rotation center axis and projecting both ends from the rolling member; A fourth rotation element capable of rotating relative to the first to third rotation elements on the first rotation center axis, wherein the fourth rotation element tilts one end of the support shaft. Sometimes the first disk part formed with a guide groove or a guide hole for guiding along the side wall in the radial direction of itself and the other end of the support shaft along the side wall in the radial direction of the support shaft when tilting In a continuously variable transmission having a second disk part in which a guide groove or guide hole is formed and a connecting member that connects the first disk part and the second disk part, the guide groove or the The guide hole is characterized in that at least one end in the radial direction is closed, and a radius of a corner of a boundary portion between the closed radial end and the side wall is set to be equal to or smaller than a radius of the support shaft. .

  Here, the side walls of the guide grooves or the guide holes are formed on the support shaft by the spin moment of the rolling member in a state where the second rotation center axis is disposed on the tilt plane of the rolling member. It is desirable to have a shape that makes the contact.

  Since the continuously variable transmission according to the present invention does not move the support shaft guided along the side wall along the corner, the rolling member is tilted while the support shaft is in contact with the side wall. The rotational axis deviation of the rolling member can be suppressed. Therefore, this continuously variable transmission can avoid a reduction in power transmission efficiency due to an unintended shift due to a rotational axis shift of the rolling member and generation of heat loss.

FIG. 1 is a partial sectional view showing an example of a continuously variable transmission according to the present invention. FIG. 2 is an explanatory view showing the shape of the guide groove of the carrier as seen from the direction of arrow A in FIG. FIG. 3 is an explanatory view of the shape of the guide groove as viewed from the inner space side of the carrier. FIG. 4 is an explanatory view of the shape of the guide groove of the carrier viewed from the direction of arrow B in FIG. FIG. 5 is a diagram illustrating the shape of the corner rounded portion of the guide groove of the carrier. FIG. 6 is a diagram illustrating an unfavorable shape of the corner rounded portion of the guide groove of the carrier. FIG. 7 is a diagram for explaining the rotational axis deviation of the planetary ball.

  Embodiments of a continuously variable transmission according to the present invention will be described below in detail with reference to the drawings. The present invention is not limited to the embodiments.

[Example]
An embodiment of a continuously variable transmission according to the present invention will be described with reference to FIGS.

  First, an example of a continuously variable transmission according to the present embodiment will be described with reference to FIG. Reference numeral 1 in FIG. 1 indicates a continuously variable transmission according to this embodiment.

  The continuously variable transmission mechanism that forms the main part of the continuously variable transmission 1 includes first to fourth rotating elements 10, 20, 30, which are capable of relative rotation with each other and have a common first rotation center axis R 1. 40, a plurality of fifth rotation elements 50 each having a second rotation center axis R2 parallel to the first rotation center axis R1 and a reference position to be described later, and first to fourth rotation elements 10, 20, This is a so-called traction planetary gear mechanism provided with a shaft 60 as a transmission rotating shaft disposed at the rotation centers 30 and 40. The continuously variable transmission 1 changes the gear ratio between input and output by inclining the second rotation center axis R2 with respect to the first rotation center axis R1 and tilting the fifth rotation element 50. . In the following, unless otherwise specified, the direction along the first rotation center axis R1 and the second rotation center axis R2 is referred to as the axial direction, and the direction around the first rotation center axis R1 is referred to as the circumferential direction. Further, the direction orthogonal to the first rotation center axis R1 is referred to as a radial direction, and among these, the inward side is referred to as a radial inner side, and the outward side is referred to as a radial outer side. In this continuously variable transmission 1, one of the first to fourth rotating elements 10, 20, 30, 40 is fixed so as not to rotate in the circumferential direction, and the rest of the elements is circumferentially It can be rotated.

  In the continuously variable transmission 1, torque is transmitted between the first rotating element 10, the second rotating element 20, the third rotating element 30, and the fourth rotating element 40 via the fifth rotating elements 50. Is called. For example, in the continuously variable transmission 1, one of the first to fourth rotating elements 10, 20, 30, and 40 serves as a torque (power) input unit, and at least one of the remaining rotating elements is Torque output section. For this reason, in this continuously variable transmission 1, the ratio of the rotation speed (the number of rotations) between any rotation element serving as the input unit and any rotation element serving as the output unit is the gear ratio. For example, the continuously variable transmission 1 is disposed on the power transmission path of the vehicle. In that case, the input part is connected with the power source side, such as an engine and a motor, and the output part is connected with the drive wheel side. In this continuously variable transmission 1, the rotation operation of each rotation element when torque is input to the rotation element as the input unit is referred to as normal drive, and the rotation element as the output unit is in the direction opposite to that during normal drive. The rotating operation of each rotating element when torque is input is called reverse driving. For example, in the continuously variable transmission 1, according to the example of the preceding vehicle, when the torque is input from the power source side to the rotating element as the input unit and the rotating element is rotated as in acceleration or the like, Driving is performed, and reverse driving is performed when torque in the opposite direction to that during forward driving is input to the rotating rotating element serving as the output unit from the driving wheel side, such as deceleration.

  In the continuously variable transmission 1, a plurality of fifth rotation elements 50 are arranged radially about the center axis (first rotation center axis R <b> 1) of the shaft 60. Each of the fifth rotating elements 50 is sandwiched between the first rotating element 10 and the second rotating element 20 that are arranged to face each other, and is disposed on the outer peripheral surface of the third rotating element 30. Each of the fifth rotation elements 50 rotates around its rotation center axis (second rotation center axis R2). Further, the fifth rotating element 50 rotates together with the fourth rotating element 40 and revolves around the first rotation center axis R1 unless the fourth rotating element 40 is the object to be fixed. Do. The continuously variable transmission 1 presses at least one of the first and second rotating elements 10, 20 against the fifth rotating element 50, thereby causing the first to fourth rotating elements 10, 20, 30, 40 to be pressed. Appropriate frictional force (traction force) is generated between the first rotary element 50 and the fifth rotating element 50, and torque can be transmitted therebetween. Further, the continuously variable transmission 1 tilts each of the fifth rotation elements 50 on a tilt plane including the second rotation center axis R2 and the first rotation center axis R1 of the first rotation element 10. The ratio of the rotational speed (rotational speed) between the input and output is changed by changing the ratio of the rotational speed (rotational speed) between the first rotating element 20 and the second rotational element 20.

  Here, in the continuously variable transmission 1, the first and second rotating elements 10 and 20 function as a ring gear as a planetary gear mechanism. The third rotating element 30 functions as a sun roller of the traction planetary gear mechanism, and the fourth rotating element 40 functions as a carrier. The fifth rotating element 50 functions as a ball-type pinion in the traction planetary gear mechanism. Hereinafter, the first and second rotating elements 10 and 20 are referred to as “first and second rotating members 10 and 20”, respectively. The third rotating element 30 is referred to as “sun roller 30”, and the fourth rotating element 40 is referred to as “carrier 40”. The fifth rotating element 50 is referred to as a “planetary ball 50”. Hereinafter, the case where the carrier 40 is the above-described fixing target will be described in detail as an example.

  The first and second rotating members 10 and 20 are disk members (disks) or ring members (rings) whose center axes coincide with the first rotation center axis R1, and each planetary ball is opposed in the axial direction. 50 is interposed. In this example, both are circular members. The first rotating member 10 forms a torque input portion (input shaft) when the continuously variable transmission 1 is driven forward together with a torque cam 71 and a first torque transmission member 81 described later. The input shaft can perform relative rotation in the circumferential direction with respect to the shaft 60 via the radial bearings RB1 and RB2. On the other hand, the second rotating member 20 forms a torque output portion (output shaft) when the continuously variable transmission 1 is driven forward together with a torque cam 72 and a second torque transmission member 82 described later. The output shaft can rotate in the circumferential direction relative to the input shaft and the shaft 60 via radial bearings RB3 and RB4. The shaft 60 exemplified here is fixed to a fixed portion of the continuously variable transmission 1 such as a vehicle body or a housing (not shown), for example, and has a cylindrical shape configured not to rotate relative to the fixed portion. It is a fixed shaft.

  Each of the first and second rotating members 10 and 20 has a contact surface that comes into contact with a radially outer peripheral curved surface of each planetary ball 50 described in detail later. Each of the contact surfaces has, for example, a concave arc surface having a curvature equal to the curvature of the outer peripheral curved surface of the planetary ball 50, a concave arc surface having a curvature different from the curvature of the outer peripheral curved surface, a convex arc surface, or a flat surface. is doing. Here, the first and second contact surfaces are formed so that the distance from the first rotation center axis R1 to the contact portion with each planetary ball 50 becomes the same length in the state of a reference position described later. The contact angles of the rotating members 10 and 20 with respect to the planetary balls 50 are the same. The contact angle is an angle from the reference to the contact portion with each planetary ball 50. Here, the radial direction is used as a reference. The respective contact surfaces are in point contact or surface contact with the outer peripheral curved surface of the planetary ball 50. Each contact surface is radially inward and oblique with respect to the planetary ball 50 when an axial force is applied from the first and second rotating members 10, 20 toward the planetary ball 50. It is formed so that the power of.

  The sun roller (idler roller) 30 has a cylindrical shape with a center axis coinciding with the first rotation center axis R1. A plurality of planetary balls 50 are radially arranged at substantially equal intervals on the outer peripheral surface of the sun roller 30. Accordingly, the outer peripheral surface of the sun roller 30 is a rolling surface when the planetary ball 50 rotates. The sun roller 30 can roll (rotate) each planetary ball 50 by its own rotation, or it can rotate along with the rolling operation (spinning) of each planetary ball 50.

  The sun roller 30 is supported by a bearing (an idler plate 31 and a bearing ball 32) so as to be freely rotatable in the circumferential direction around the first rotation center axis R1. The idler plate 31 is a cylindrical member having a central axis coinciding with the first rotation central axis R1, and supports the sun roller 30 via a bearing ball 32 in a circumferential groove on the outer peripheral surface thereof. The idler plate 31 can be moved relative to the shaft 60 inserted inward in the axial direction. The sun roller 30 can be reciprocated in the axial direction by a shift mechanism via the idler plate 31. The amount of movement of the sun roller 30 is proportional to the tilt angle of each planetary ball 50.

  The shift mechanism forms part of a tilting device that tilts the planetary ball 50. The shift mechanism includes a hollow portion 61 of the shaft 60, a slit 62 of the shaft 60 that allows communication between the hollow portion 61 and the outer peripheral surface of the shaft 60, a shift shaft 91 inserted into the hollow portion 61, and the shift shaft. And a shift key 92 having a cylindrical portion screwed to the outer peripheral surface of 91. The shift shaft 91 moves in the circumferential direction relative to the shaft 60 using an actuator such as an electric motor as a drive source. Further, the shift key 92 has its plate-like key portion protruding from the slit 62 toward the idler plate 31 and fixed to the inner peripheral surface side of the idler plate 31. This shift mechanism moves the key portion of the shift key 92 in the slit 62 in the axial direction as the shift shaft 91 rotates. Therefore, the shift mechanism can move the sun roller 30 together with the idler plate 31 and the bearing ball 32 relative to the shaft 60 in the axial direction. Since the key portion of the shift key 92 is locked by the wall surface on the circumferential direction side of the slit 62, the idler plate 31 does not rotate relative to the shaft 60 in the circumferential direction.

  The carrier 40 is, for example, arranged so as to oppose the first and second disk parts 41, 42 having the center axis coinciding with the first rotation center axis R1, and the first and second disk parts 41, 42 are arranged. A plurality of connecting shafts (not shown) are connected to form a bowl shape as a whole. As a result, the carrier 40 has an open portion on the outer peripheral surface. Each planetary ball 50 is disposed between the first and second disk portions 41 and 42, and a part protrudes radially outward from the outer peripheral surface of the carrier 40 through the open portion. Guide grooves 43 and 44 for guiding the end of the support shaft 51 of the planetary ball 50 in the tilting direction (radial direction) are respectively provided in the opposing portions of the first and second disk portions 41 and 42. Is formed. The guide grooves 43 and 44 are formed for each planetary ball 50 with the longitudinal direction thereof aligned with the radial direction. That is, all the guide grooves 43 and all the guide grooves 44 are radially formed when viewed from the axial direction.

  The planetary ball 50 is a rolling member that rolls on the outer peripheral surface of the sun roller 30. The planetary ball 50 is preferably a perfect spherical body, but it may have a spherical shape at least in the rolling direction, for example, a rugby ball having an elliptical cross section. The planetary ball 50 is rotatably supported by a support shaft 51 that passes through the center of the planetary ball 50. For example, the planetary ball 50 can rotate relative to the support shaft 51 with the second rotation center axis R2 as a rotation axis (that is, rotate) by a bearing (not shown) disposed between the outer periphery of the support shaft 51. I am doing so. Accordingly, the planetary ball 50 can roll on the outer peripheral surface of the sun roller 30 around the support shaft 51. Both ends of the support shaft 51 are projected from the planetary ball 50.

  The reference position of the support shaft 51 is a position where the second rotation center axis R2 is parallel to the first rotation center axis R1, as shown in FIG. The support shaft 51 is tilted from the reference position and within the tilt plane including the rotation center axis (second rotation center axis R2) and the first rotation center axis R1 formed at the reference position. It can swing (tilt) with the planetary ball 50 between the positions. The tilt is performed with the center of the planetary ball 50 as a fulcrum in the tilt plane.

  The continuously variable transmission 1 is provided with a shift control unit that shifts each planetary ball 50 by tilting. As a speed change control unit serving as a tilting device for the planetary ball 50, those known in this technical field can be used. For example, the shift control unit includes the shift mechanism described above, the idler plate 31, and the tilting arm 93.

  The tilting arm 93 causes a tilting force to act on the support shaft 51 and the planetary ball 50 as the idler plate 31 moves in the axial direction, and the second rotation center axis R2 of the planetary ball 50 is moved along with the support shaft 51. For tilting. This tilting arm 93 is a member extending in the radial direction, and the tip portion on the radially inner side is formed into a tapered shape. The tilting arm 93 is prepared for each end portion of all the support shafts 51, and a radially outer portion is attached to the end portion of the support shaft 51. Therefore, the planetary ball 50 is supported by a pair of tilting arms 93 and 93 that hold the end portions of the protruding support shaft 51. Further, the tilting arm 93 is arranged between the first disk portion 41 and the idler plate 31 and the planetary ball 50 and between the second disk portion 42 and the idler plate 31 and the planetary ball 50 in the internal space of the carrier 40. Set up. Therefore, all the tilting arms 93 on the first disk part 41 side and all the tilting arms 93 on the second disk part 42 side are respectively radial when viewed from the axial direction. The tilting arm 93 does not move relative to the carrier 40 in the axial direction or rotate in the circumferential direction.

  The pair of tilting arms 93 sandwich the wall surfaces of both end portions in the axial direction of the idler plate 31 between the radially inner tapered wall surfaces. Here, the idler plate 31 is tapered toward the outside in the radial direction. On the other hand, the pair of tilting arms 93 has a radially outwardly opening shape sandwiching the tapered shape of the idler plate 31 by the tapered shape of each tip portion thereof. As a result, the shift control unit moves the idler plate 31 in the axial direction by the action of the shift mechanism, so that the taper-shaped wall surface of each tilting arm 93 from the taper-shaped wall surface with respect to the axial direction. A force directed diagonally outward is applied. Along with this, the tilting arm 93 groups on the first disk portion 41 side and the second disk portion 42 side tilt the respective support shafts 51 in the tilting plane, and each planetary ball 50 is also moved along with this. Tilt in the tilt plane. At that time, both ends of each support shaft 51 are guided in the radial direction by the guide grooves 43 and 44.

  In this continuously variable transmission 1, when the tilt angle of each planetary ball 50 is the reference position, that is, 0 degrees, the first rotating member 10 and the second rotating member 20 have the same rotational speed (the same rotational speed). Rotate with. That is, at this time, the rotation ratio (ratio of rotation speed or rotation speed) between the first rotation member 10 and the second rotation member 20 is 1, and the transmission ratio is 1. On the other hand, when each planetary ball 50 is tilted from the reference position, the contact portion (contact point) with the first rotating member 10 and the contact portion (contact point) with the second rotating member 20 are changed and supported. The distance from the central axis of the shaft 51 to the contact portion with the first rotating member 10 changes, and the distance from the central axis of the support shaft 51 to the contact portion with the second rotating member 20 changes. Therefore, one of the first rotating member 10 and the second rotating member 20 rotates at a higher speed than when it is at the reference position, and the other rotates at a lower speed. For example, the second rotating member 20 has a lower rotation (deceleration) than the first rotating member 10 when the planetary ball 50 is tilted in one direction, and the first rotating member 10 is tilted in the other direction. (High speed). Therefore, in the continuously variable transmission 1, the rotation ratio (transmission ratio) between the first rotating member 10 and the second rotating member 20 can be changed steplessly by changing the tilt angle. . At the time of the speed increase here, the upper planetary ball 50 in FIG. 1 is tilted in the clockwise direction on the paper and the lower planetary ball 50 is tilted in the counterclockwise direction on the paper. Further, at the time of deceleration, the upper planetary ball 50 in FIG. 1 is tilted counterclockwise on the paper surface and the lower planetary ball 50 is tilted clockwise on the paper surface.

  In this continuously variable transmission 1, at least one of the first or second rotating members 10, 20 is pressed against each planetary ball 50, so that the first and second rotating members 10, 20 and each planetary planet are transmitted. A pressing portion that generates a pinching force between the ball 50 and the ball 50 is provided. The pressing part generates an axial force (pressing force) to generate a pinching force therebetween. In the meantime, an appropriate frictional force (traction force) is generated by the clamping pressure. Further, the pressing force of the pressing portion is also applied to the sun roller 30 via each planetary ball 50 depending on the shape and positional relationship between the contact surfaces of the first and second rotating members 10 and 20 and the outer peripheral curved surface of each planetary ball 50. It is transmitted. For this reason, an appropriate frictional force (traction force) is also generated between the sun roller 30 and each planetary ball 50. In the continuously variable transmission 1, it is possible to efficiently transmit rotational torque by the frictional force. This pressing portion is based on which rotational element of the continuously variable transmission 1 is on the torque input side and the rotational direction of the input torque, and / or one of the first rotating member 10 side and the second rotating member 20 side. Should be provided. In this example, a torque cam mechanism as a pressing portion is provided on both sides.

  The torque cam 71 on the first rotating member 10 side is disposed between the first rotating member 10 and the first torque transmitting member 81. For example, the torque cam 71 transmits the rotational torque of the first torque transmission member 81 to the first rotation member 10 and generates axial thrust from the first torque transmission member 81 toward the first rotation member 10. In addition, the rotational torque of the first rotating member 10 is transmitted to the first torque transmitting member 81, and an axial thrust from the first rotating member 10 toward the first torque transmitting member 81 is generated. The first torque transmission member 81 has a cylindrical portion that enables relative rotation in the circumferential direction with respect to the shaft 60 via the radial bearings RB1 and RB2. Here, a power source is connected to the cylindrical portion.

  On the other hand, the torque cam 72 on the second rotating member 20 side is disposed between the second rotating member 20 and the second torque transmitting member 82. For example, the torque cam 72 transmits the rotational torque of the second rotating member 20 to the second torque transmitting member 82 and generates an axial thrust from the second rotating member 20 toward the second torque transmitting member 82. In addition, the rotational torque of the second torque transmitting member 82 is transmitted to the second rotating member 20, and the axial thrust from the second torque transmitting member 82 toward the second rotating member 20 is generated. The second torque transmission member 82 has a two-part structure for the convenience of transmission assembly, and one of the second torque transmission members 82 is relative to the first torque transmission member 81 via the radial bearing RB3 and the thrust bearing TB. Rotation is possible, and the other is rotatable relative to the shaft 60 via a radial bearing RB4 and an outer case 204 described later.

  In the continuously variable transmission 1, a frictional force (traction force) is generated between the first rotating member 10 and each planetary ball 50 as the first rotating member 10 rotates, and each planetary ball 50 rotates. Begin. In the continuously variable transmission 1, due to the rotation of each planetary ball 50, a frictional force is also generated between each planetary ball 50 and the second rotating member 20 and between each planetary ball 50 and the sun roller 30. The second rotating member 20 and the sun roller 30 start rotating.

  In the continuously variable transmission 1, a frictional force is generated between the second rotating member 20 and each planetary ball 50 as the second rotating member 20 rotates, and each planetary ball 50 begins to rotate. . In the continuously variable transmission 1, due to the rotation of each planetary ball 50, a frictional force is also generated between each planetary ball 50 and the first rotating member 10 and between each planetary ball 50 and the sun roller 30. The first rotating member 10 and the sun roller 30 start rotating.

  In this example, the first rotating member 10 is on the input side and the second rotating member 20 is on the output side. However, when the sun roller 30 is on the input side by allowing the shaft 60 to rotate, the sun roller 30 A frictional force is generated between the sun roller 30 and each planetary ball 50 with the rotation, and each planetary ball 50 starts to rotate. In the continuously variable transmission 1 in this case, the rotation of the respective planetary balls 50 causes the rotation between the planetary balls 50 and the first rotation member 10, and between the planetary balls 50 and the second rotation member 20. A frictional force is also generated, and the first rotating member 10 and the second rotating member 20 also start to rotate. Further, when a rotating element other than the carrier 40 is set as a fixed object, each planetary ball 50 starts to rotate and revolve as the carrier 40 rotates. In the continuously variable transmission 1 in this case, the rotation of the respective planetary balls 50 causes the rotation between the planetary balls 50 and the first rotation member 10, and between the planetary balls 50 and the second rotation member 20. A frictional force is also generated between each planetary ball 50 and the sun roller 30, and the first rotating member 10, the second rotating member 20, and the sun roller 30 also start to rotate.

  In the continuously variable transmission 1 configured as described above, when the power of the power source is applied to the first rotating member 10, the contact portion of the planetary ball 50 with the first rotating member 10 is in contact with the first rotating member 10. A tangential friction force (traction force) is applied in the same direction as the rotation direction (opposite to the rotation direction of the planetary ball 50 in a state where the spin moment is not applied). Furthermore, in this case, the contact force between the planetary ball 50 and the second rotation member 20 is opposite to the frictional force of the contact portion with the first rotation member 10, that is, the rotation direction of the second rotation member 20. A frictional force in the reverse direction (the same direction as the rotation direction of the planetary ball 50 in a state where the following spin moment does not act) is applied. That is, during the operation of the continuously variable transmission 1, as shown in FIG. 2, the friction in the reverse direction occurs between the contact portion of the planetary ball 50 with the first rotating member 10 and the contact portion of the second rotating member 20. Force is constantly generated. Here, as shown in FIG. 2, the respective contact portions are located on the outer peripheral surface of the planetary ball 50 at a position deviated from the center of gravity of the planetary ball 50. For this reason, each frictional force becomes an eccentric load in the planetary ball 50, and therefore when the frictional force is applied, a rotational moment centered on the center of gravity (hereinafter referred to as “spin moment”) is the planetary ball 50. Occurs. Here, a spin moment having a counterclockwise moment is generated. 2 shows the contact portion between the planetary ball 50 having a tilt angle of 0 degrees and the first and second rotating members 10 and 20 from the direction of the arrow A in FIG. It is the figure seen from the direction which is parallel with respect to and orthogonal to 2nd rotation central axis R2.

  By the way, in this continuously variable transmission 1, in order to smooth the tilting operation of the planetary ball 50, a gap is provided between members that are operated during the tilting operation. For example, in this example, the groove widths of the guide grooves 43 and 44 of the carrier 40 are made larger than the outer diameter of the support shaft 51, and a gap is formed between each end of the support shaft 51 and the guide grooves 43 and 44. Provided. When a guide member (for example, a sphere) in the guide grooves 43 and 44 is disposed at the end of the support shaft 51, the groove width of the guide grooves 43 and 44 is the guide member or the support shaft 51. Enlarge than the largest part of the. Hereinafter, the support shaft 51 including the guide member is collectively referred to. Here, in the continuously variable transmission 1, if the second rotation center axis R2 of the planetary ball 50 deviates from the above-described tilt plane due to the clearance and the spin moment, the first rotation center axis R1 and The parallel state between the two may be lost, and a skew due to the rotational axis deviation of the planetary ball 50 may occur, which may cause unintended shifts and heat loss. For this reason, the continuously variable transmission 1 is provided with a rotation axis deviation suppressing unit that suppresses the rotation axis deviation of the planetary ball 50 and performs the tilting operation of the planetary ball 50 in the above-described inclination plane.

  The rotation axis deviation suppressing portion is constituted by the support shaft 51 of the planetary ball 50 and at least one of the guide grooves 43 and 44 of the carrier 40. This rotational axis deviation suppression unit is prepared for each planetary ball 50.

  For example, the rotation axis deviation suppression portion composed of the guide groove 43 and the support shaft 51 of the first disk portion 41 uses the groove side wall 43a with which the support shaft 51 abuts by a spin moment as a locking surface for suppressing the rotation axis deviation. Use. As shown in FIG. 3, the groove side wall 43a is formed on the support shaft 51 of the planetary ball 50 when the second rotation center axis R2 of the planetary ball 50 is tilting in the tilt plane. A shape in which the outer peripheral surface continues to abut. That is, the groove side wall 43a has a wall surface parallel to the tilt plane at a position shifted in the moment direction of the spin moment by the radius of the support shaft 51 with respect to the tilt plane. The guide groove 43 may have a groove width wider than the outer diameter of the support shaft 51 with the groove side wall 43a as a base point. FIG. 3 is a view of the first disk portion 41 and the second disk portion 42 as viewed from the inside of the carrier 40 (that is, the planetary ball 50 side).

  The same applies to the case where the rotation axis deviation suppressing portion is provided on the guide groove 44 side of the second disk portion 42. The groove side wall 44a with which the support shaft 51 abuts by the spin moment is the planetary ball 50 within the tilt plane. When the second rotation center axis R2 is tilting, the outer peripheral surface of the support shaft 51 of the planetary ball 50 is kept in contact. That is, the groove side wall 44a also has a wall surface parallel to the tilt plane at a position shifted in the moment direction of the spin moment by the radius of the support shaft 51 with respect to the tilt plane. The guide groove 44 may have a groove width wider than the outer diameter of the support shaft 51 with the groove side wall 44a as a base point.

  In the continuously variable transmission 1, such a rotational axis deviation suppressing portion is provided on at least one of the first disc portion 41 side and the second disc portion 42 side, so that the rotational axis of the planetary ball 50 due to the spin moment is provided. Deviation can be suppressed. Therefore, the continuously variable transmission 1 can prevent unintentional shift and heat loss due to the rotational axis shift of the planetary ball 50, and can suppress a decrease in torque transmission efficiency.

  Here, in the continuously variable transmission 1, since the rotation axis deviation suppressing portion is provided on both the first disc portion 41 side and the second disc portion 42 side, the guide grooves 43 and 44 are formed as shown in FIG. When the carrier 40 is viewed from the axial direction (the direction of arrow B in FIG. 1), a part thereof overlaps. The guide grooves 43 and 44 maintain the parallel state of the first rotation center axis R1 and the second rotation center axis R2, and the width in the circumferential direction of the overlapping portion (guide overlap portion) is the outer diameter of the support shaft 51. To be equivalent to Accordingly, in the planetary ball 50, the rotation axis shift due to the spin moment is suppressed by arranging the support shaft 51 in the guide overlap portion. Further, the end portion on the radially outer side of the guide overlap portion is made to coincide with the position of the end portion of the support shaft 51 when the planetary ball 50 has the maximum tilt angle, or slightly outward in the radial direction from the position. Set. Note that FIG. 4 shows the guide grooves 43 and 44 as a perspective view. For convenience of comparison, the guide groove 43 is indicated by a one-dot chain line and the guide groove 44 is indicated by a two-dot chain line.

  As described above, the guide grooves 43 and 44 have the guide overlap portions, that is, the groove side walls 43a and 44a, so that the rotation axis shift of the planetary ball 50 due to the spin moment is prevented without hindering the smooth tilting operation of the planetary ball 50. Suppressed. Here, the guide grooves 43 and 44 close both ends in the radial direction, and when viewed from the axial direction, the guide grooves 43 and 44 have a rectangular shape (window shape) in which the longitudinal direction coincides with the radial direction. For this reason, the guide groove 43 has a corner portion which is a boundary portion between the groove side walls 43a and 43b and the radial end portions 43c and 43d as shown in FIG. Are formed as corner rounded portions C1 to C4. Similarly, the corners C1 to C4 are also provided in the guide groove 44 at the boundary between the groove side walls 44a and 44b and the radial ends 44c and 44d.

  In the guide groove 43 of the present embodiment, as shown in FIG. 5, the radii r1 and r2 of at least the corner radius portions C1 and C2 at both ends of the groove sidewall 43a among all corner radius portions C1 to C4 are supported by the support shaft 51. The radius rs is less than or equal to rs (r1 ≦ rs, r2 ≦ rs). That is, in this guide groove 43, the radius r1 of the corner radius portion C1 between the groove side wall 43a that guides the support shaft 51 and the radially outer end 43c at the time of tilting, the groove side wall 43a and the radially inner side The radius r2 of the corner rounded portion C2 between the end portion 43d and the support shaft 51 is set to be equal to or less than the radius rs. Similarly, the radius r1, r2 of at least the corner round portions C1, C2 at both ends of the groove side wall 44a among the corner round portions C1-C4 is set to be equal to or smaller than the radius rs of the support shaft 51. (R1 ≦ rs, r2 ≦ rs).

  For example, when the radii r1 and r2 of the corner rounded portions C1 and C2 are larger than the radius rs of the support shaft 51, the support shaft 51 guided along the groove side walls 43a and 44a as shown in FIG. Moves along the corner rounded portions C1 and C2, and the second rotation center axis R2 deviates from the tilt plane. In other words, in this case, when the planetary ball 50 tilts to the maximum tilt angle at the time of acceleration or deceleration or close to it, as shown in FIG.

  However, by setting the radii r1 and r2 of the corner round portions C1 and C2 to be equal to or smaller than the radius rs of the support shaft 51, the support shaft 51 is guided along the groove side walls 43a and 44a during the tilting, and the planetary ball 50 is accelerated. When the maximum tilt angle at the time of deceleration or deceleration is reached, the support shaft 51 has the second rotation center axis R2 deviated from the tilt plane, and the radially outer ends 43c, 44c or the radially inner side. It is possible to reach the end portions 43d and 44d. That is, in the continuously variable transmission 1, the planetary ball 50 can be tilted while the support shaft 51 is in contact with the groove side walls 43a and 44a. Therefore, the guide grooves 43 and 44 of the present embodiment hinder smooth tilting operation of the planetary ball 50 within the tilting range of the planetary ball 50 by the groove side walls 43a and 44a and the corner round portions C1 and C2. In addition, the rotational axis shift of the planetary ball 50 due to the spin moment can be suppressed. Therefore, the continuously variable transmission 1 can prevent unintentional shift and heat loss due to the rotational axis shift of the planetary ball 50 within the tilting range of the planetary ball 50, and decrease the torque transmission efficiency. Can be suppressed.

  In the present embodiment, the guide grooves 43 and 44 whose both ends in the radial direction are closed are illustrated, but the guide groove is one of the guide grooves 43 and 44 in the radial direction (the end portions 43c and 44c or 44). It may be closed at the ends 43d, 44d) and the other opened. Even in this case, the guide grooves on the first disk portion 41 side and the second disk portion 42 side have a shape in which the above-described guide overlap portion is provided, and the groove side wall 43a and the end portion (end portion). 43c or end 43d), and the radius of the corner R between the groove side wall 44a and the end (end 44c or end 44d) is larger than the radius rs of the support shaft 51. Make it smaller. Thereby, even if it is such a guide groove, the continuously variable transmission 1 can have the same effect as the guide grooves 43 and 44. In addition, one of the guide grooves 43 and 44 may be replaced with a guide groove that is open at one end in the radial direction. In this case, the same effect can be obtained.

  Furthermore, in the present embodiment, the guide grooves 43 and 44 having the groove bottom are illustrated, but the guide grooves 43 and 44 are replaced with the guide grooves 43 and 44 as the guide portions of the support shaft 51 at the time of tilting. Alternatively, a guide hole in which the groove bottom is omitted or a guide hole in which the groove bottom is omitted from the above-described guide groove having one end in the radial direction opened may be used. Even in this case, the guide hole can bring the same effect as the guide grooves 43 and 44 to the continuously variable transmission 1. Further, one of the guide grooves 43 and 44 may be replaced with a guide hole, and in this case, the same effect can be obtained.

  Here, one specific application example of the continuously variable transmission 1 will be described. As a specific example, it has a function (power running function) as an electric motor that converts electrical energy into mechanical energy and outputs it, and a function as a generator (regenerative function) that converts mechanical energy into electrical energy. It can be applied to a rotating electrical machine with a built-in speed change function. Reference numeral 200 in FIG. 1 denotes the rotating electric machine with a built-in shift function.

  The rotating electrical machine 200 includes a motor generator unit 201 as a rotating electrical machine main body and the above-described continuously variable transmission 1 as a transmission unit. In the rotating electrical machine 200, each element is positioned so that the rotation center of a stator 202 and a rotor 230, which will be described later, in the motor generator section 201 and the rotation center of the continuously variable transmission 1 coincide with each other on the first rotation center axis R1. Yes.

  In this rotating electrical machine 200, the motor generator unit 201 is formed in a cylindrical shape coaxial with the first rotation center axis R1 as a whole, and at the radially inner side of this motor generator unit 201 (that is, the inner side of the motor generator unit 201). The continuously variable transmission 1 is arranged on the inner side of the peripheral surface, and the continuously variable transmission 1 is covered with the motor generator unit 201 on the radially outer side. In the rotating electric machine 200, the second torque transmission member 82 of the continuously variable transmission 1 is used as the rotor 230 of the motor generator unit 201. A stator 202 is disposed outside the rotor 230 in the radial direction. The stator 202 includes a stator coil 203 arranged radially on the outer peripheral surface of the rotor 230 and an outer case 204 covering these. The outer case 204 is fixed to the shaft 60.

  As described above, the continuously variable transmission according to the present invention is useful for a technique capable of suppressing the rotational axis shift of the rolling member.

1 continuously variable transmission 10 first rotating member (first rotating element)
20 Second rotating member (second rotating element)
30 Sun Roller (third rotating element)
40 Carrier (4th rotating element)
41 1st disk part 42 2nd disk part 43,44 Guide groove 43a, 44a Groove side wall 43c, 43d, 44c, 44d End part 50 Planetary ball (rolling member)
51 Support shaft C1 to C4 Corner rounded portion R1 First rotation center axis R2 Second rotation center axis

Claims (2)

First and second rotational elements that are relatively rotatable and have a common first rotational center axis disposed opposite to each other;
A rolling member having a second rotation center axis parallel to the first rotation center axis, and a plurality of radial members arranged radially about the first rotation center axis and sandwiched between the first and second rotation elements When,
By changing the respective contact points between the first rotating element and each rolling member and the respective contact points between the second rotating element and each rolling member by the tilting operation of each rolling member, A shift control unit that changes a rotation ratio between the rotating elements;
A third rotating element that is arranged on the outer peripheral surface and capable of rotating relative to the first and second rotating elements on the first rotation center axis;
A support shaft of the rolling member having the second rotation center axis and projecting both ends from the rolling member;
A fourth rotating element capable of rotating relative to the first to third rotating elements on the first rotation center axis;
With
The fourth rotating element includes a first disk portion formed with a guide groove or a guide hole that guides one end portion of the support shaft along its side wall in a radial direction of the support shaft when tilting, and the support shaft. A second disk part formed with a guide groove or a guide hole for guiding the other end part in the radial direction along the side wall at the time of tilting, and a connection for connecting the first disk part and the second disk part A continuously variable transmission having a member;
Each of the guide groove or the guide hole closes at least one end in the radial direction, and the radius of the corner of the boundary portion between the closed end in the radial direction and the side wall is smaller than the radius of the support shaft. A continuously variable transmission characterized by that.   Each of the guide grooves or the side walls of the guide holes abuts the support shaft by a spin moment of the rolling member in a state where the second rotation center axis is disposed on a tilt plane of the rolling member. The continuously variable transmission according to claim 1, wherein the continuously variable transmission has a shape to be formed.

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